Control device for fluid fuel burners



Dec. 22, 1959 R. F. GARNER 2,918,088

CONTROL DEVICE FOR FLUID FUEL BURNERS Filed July 17, 1957 3 Sheets-Sheet l Dec. 22, 1959 R. F. GARNER 2,918,088

CONTROL DEVICE FOR FLUID FUEL BURNERS Filed July 17, 1957 3 Sheets-Sheet 2 L-J T P I N V EN TOR.

By Easel/1 5012781. WM

HIS ATZIUMEY' Dec. 22, 1959 R. F. GARNER 2,918,088

CONTROL DEVICE FOR FLUID FUEL BURNERS Filed July 17, 1957 3 Sheets-Sheet 3 mom).

CONTROL DEVICE FOR FLUID FUEL BURNERS Application July 17, 1957, Serial No. 672,390

7 (Ilaims. (Cl. 137630.19)

This invention relates to control devices for fluid fuel I burning apparatus and more particularly to multi-valve devices for sequentially controlling the flow of fuel to a plurality of burners or the like.

An object of the invention is to arrange a main burner valve, an afterburner valve and a timing mechanism for controlling the sequential operation of both valves within a single casing.

Another object of the invention is to utilize a common actuating member for controlling the operation of the valves and for setting the timing mechanism.

Another object of the invention is to arrange the components of the device to insure ready access for servicing.

Still another object of the invention is to utilize snap acting valve members for controlling the flow of fuel to a pair of burners on a fixed timing cycle.

This invention finds particular utility in sequentially actuated valves for fluid fuel burning incinerators of the type having a main burner and an afterburner located on the flue or stack. In apparatus of this general character, a main burner is utilized to burn various disposables placed therein, and an afterburner is employed to effect combustion of the gases expelled from the main burner chamber. In this manner, the noxious vapors and gases expelled from the main incinerator chamber are burned in an afterburning chamber or flue to reduce the combustible material which was not completely oxidized in the main burner to thereby somewhat reduce the obnoxious character of the exhaust prior to the time these gases reach the outside atmosphere.

In a broad aspect, the present invention contemplates a single control device for automatically controlling the flow of fuel to a main burner and an afterburner. In the preferred embodiment of the invention, the control device is comprised of a pair of valve members and a timer controlled actuator therefor arranged within a single casing to control fuel flow from a source through a pair of easing outlets. To set the device in operation, the timer controlled actuator is manually moved through a predetermined range of movement to open one of the valve members and close the other to permit fuel to enter the casing and flow through only one outlet during a first predetermined time interval. At the end of this predetermined time interval, the other valve is also moved to the open position where it remains during a second predetermined time interval to permit flow of fuel through both casing outlets. Upon the termination of the second time interval, the first mentioned valve is again moved to the closed position to prevent the flow of fuel into the casing and thereby terminate the flow of fuel through both casing outlets.

Other objects and advantages of the invention will appear from the following description taken in conjunction with the accompanying drawings wherein:

Fig. 1 is a front elevation of the control device;

Fig. 2 is a side elevation of the control device;

Fig. 3 is a side elevation of a detail;

Fig. 4 is a section taken along line IV--IV of Fig. 3;

States Patent O 'ice Fig. 5 is a section similar to Fig. 4 with the parts in a different position;

Fig. 6 is a section taken along the line VIVI of Fig. 1.

and 6, the control device includes a casing 10 provided with an inlet passage 11 (Fig. 6) and a pair of outlet passages 12 and 13 therein (Fig. 2). Inlet passage 11 is defined by a hollow internally threaded boss 14 on the casing 10 which is adapted to receive a threaded conduit or the like (not shown) for connecting the inlet passage 11 to a source of fuel (not shown). Outlet passages 12 and 13 are also defined by a pair of hollow, internally threaded bosses 15 and 16, respectively, on the casing 10 which are likewise adapted to receive threaded conduits or the like (not shown) for connecting the outlet passages 12 and 13 to a pair of burners or the like (not shown), such as (in this instance) an incinerator afterburner and main burner, respectively.

Casing 10 is provided with a plurality of chambers therein including a centrally disposed chamber 18 which communicates with outlet passage 12. A valve chamber 20 is formed interiorly of the casing 10 in communication with inlet passage 11 by a longitudinally extending wall 22 integral with and projecting from casing end wall 24 and a wall 26 integral with and extending transversely from casing side wall 28. The wall 22 is provided with an enlarged aperture 30 therein to permit the flow of fuel between inlet passage 11 and chamber 18 and is provided with an annular projection 32 thereon in chamber 20 which functions as a valve seat.

A disc valve member 34 is positioned within chamber 20 and is mounted on a valve stem generally indicated by the reference numeral 36 for movement therewith between open and closed positions relative to the seat 32. The valve member 34 is normally biased toward the seat 32 by a coil spring 38 held in compression between the valve member 34 and a closure cap 40 threaded in the casing side wall 28. The valve stem 36 has an axial bore 42 extending from one end thereof for the greater portion of its length which slidably receives a centering pin 44 carried by the cap 4% for guiding the reciprocable movement of the valve member 34.

A valve chamber 46 communicating with outlet passage 13 is also formed interiorly of the casing 16 by an inner wall 48 integral with and projecting from casing end wall 50 and an inner wall 52 integral with and ex* tending transversely from casing side wall 28. The wall 48 is provided with an enlarged aperture 54 therein to permit the flow of fuel between inlet passage 11 and chamber 46 and is, also, provided with an annular projection 56 thereon in chamber 46 which functions as a valve seat.

A disc valve member 58 is positioned within chamber 46 and is mounted on a valve stem, generally indicated by the reference numeral 66, for movement therewith between open and closed positions relative to the valve seat 56. The valve member 58 is normally biased toward the seat 56 by a coil spring 62 held in compression between the valve member 58 and a closure cap' 64 threaded in the casing side wall 28. A stem 66, similar to the stem 44, is mounted in the cap 64 and is slidably received in a bore 67 in the valve stem 60 forguiding the movement of the valve member 58.

One side of the casing 10 is closed by means of a housing or .cover member 68. Housing 68 is rigidly sccured to the casing 1th by any suitable means such as a plurality of bolts 74 in this instance eight (only four 124 and fastened thereto.

shown), with four (only two shown) of the bolts 70 extending through pairs of apertured ears 72 (only one pair shown) projecting from the housing 68 and being received in threaded passages (not shown) in pairs of ribs 74 (Fig; 2, only one pair shown) projecting from the exterior surfaces of the opposed side walls 76 and 78 of the casing 10. The housing 68 in this instance is also provided with four recesses 80, 82, 84, and 86 therein to permit the use of shorter bolts in securing the housing 68 to the casing 10. A gasket or the like 88 is positioned between the mating faces 90 and 92 of the casing and housing 68, respectively, to prevent the possible leakage of fuel therebetween.

Referring to Figs. 3-6, wall 94 of housing 68 is provided with a projection 96 thereon having an axially extending bore or chamber 98 therein. Chamber 9S communicates at one end thereof with an aperture 100 in the end wall 102 of projection 96 and communicates .at the opposite end thereof with a recess 104 in the exterior surface of housing wall 94. Adjacent to projection 96 and longitudinally spaced therefrom, a casing wall 94 is provided with a pair of opposed bosses 106 and 108 thereon. Longitudinally spaced from bosses'106 and 108, casing wall 94 has another projection 110 extending therefrom.

Secured to bosses 106 and 108 by any suitable means; such as bolts 112 and 114, is a bridge 116 having pins 118 and 120 extending between the side walls 122 and The bridge 116 is adapted to extend into chamber 18 and has a U-shaped opening 121 which communicates with afterburner outlet 12 when the housing 68 is assembled.

A main burner valve lever 126 having flanges 128 extending substantially at right angles to the lever'126 is pivotally secured to pin 118 by ears 130. The flange 128 adjacent bridge wall 122 is provided with a latch portion 129. A compression spring 132 is mounted at one end on a projection 134 punched in lever 126 and at the other end on the projection 110 extending from casing wall 94 and normally biases lever 126 in a clockwise direction.

An inlet valve lever 136 extending in the opposite direction from lever 126 is pivotally mounted on pin 118 between ears 130 and the bridge side walls 122 and 124 and has an upwardly extending latch portion 137 similar to latch portion 129 of lever 126 but positioned adjacent bridge wall 124. The inlet valve lever 136 is provided with a pair of hook-like portions 138 on flanges 140 which are formed substantially at right angles to the lever 136 and these hook-like portions 138 are adapted to engage flanges 128 on lever 126 and therefore are movable in one direction therewith.

The arrangement of the parts is such that when housing or cover member 68 is assembled, pivotal movement of the valve levers 126, 136 will cause opening or closing of the main burner and inlet valves respectively.

Actuating means 141 for pivoting the levers 126, 136

is shown here as including a shaft 142 which is slidably extended through aperture 100 in projection 96 and recess 104 in the housing wall 94. Securely mounted approximately midway on the shaft 142 is a collar 144 which is adapted to engage lever 126 on movement toward casing side wall 28 and thereby pivot levers 126, 136 in a counterclockwise direction.

One end of shaft 142 has a threaded portion 146 adapted to receive an adjustable threaded head member 148 which has a collar 150 integrally formed therewith. A spring 152 is compressed between the collar 150 and a punched projection 154 in the bridge 116 and normally urges shaft 142 toward aperture 100.

A pair of latches 156 and 158, each having a recessed under portion 160, are rotatably mounted on pin 120 and are biased in a counterclockwise direction by springs '162 and 164, respectively. When the levers 126 and 136 are pivoted in a counterclockwise direction due to movement of collar 144, latch portions 128 and 137 communicate with the recessed under portions 160 of latches 156 and 158 respectively, and prevent the return of levers 126 and 127 to their original position.

However, latches 156 and 158 are provided with dissimilar release arms 166 and 168 (as best shown in Figs. 4 and 5) which extend beneath collar 150. Because of the difference in shape of these release arms, as shaft 142 moves toward aperture 100, collar 150 will engage, first a release arm 166 to rotate latch 156 clockwise to release lever 126, and then, upon further movement will engage release arm 168 to rotate latch 158 in a clockwise direction to release lever 136. It is therefore apparent that there will be a sequential release of levers 126, 136.

To prevent leakage of fluid fuel, referring more partioularly to Fig. 6, chamber 98 is supplied with suitable packing 170 which is biased against end wall 102 by spring 172. A short cylindrical member 174 with an integral collar 176 which registers with recess 104 is provided to guide the shaft 142 on its reciprocal movement. Shaft 142 is recessed at end 178 to loosely receive the end of a plunger 180. The plunger 180 extends slidably through aperture 182 of plate 184 which is secured to wall 94 of housing 68 by bolts 185 (Fig. l) and holds the packing assembly in place. The plunger 180 also slidably extends through housing 186 which is mounted on plate 184 in axial alignment with the shaft 142 and is loosely retained at the other end to a shaft 188 which is adapted to rotate and translate relative to the housing 186. Secured to the end of the shaft 188 which extends out of the housing 186 is a manually relatively stationary detent member is engageable with the projections 196, 198 for limiting axial movement of the shaft 188 and comprises a generally annular cam assembly 200 including a radial flange block 202 which is adapted to be seated in a suitable recess 204 formed in housing 186 and retained therein by screws (not shown).

As shown in Fig. 8, an annular body portion 206 extends axially inwardly from the flange 202 concentric with the shaft 188 with the end portion thereof being shaped to define a first pair of axially spaced helical surfaces 210, 212 having equal helical angles for cooperating with the follower 196 and a second pair of axially spaced helical surfaces 214, 216 having equal helix angles for cooperation with the follower 198. Helix angle and lead of the surfaces 210, 214 are equal and oppositely disposed with respect to the shaft 188. In the same manner, helix angle and lead to the surfaces 212, 216 are equally and oppositely disposed with respect to the shaft 188.

Angular extensions of the surfaces 210 through 216 may be of any suitable value depending upon particular time cycles and timer mechanism used as will become apparent hereinafter. For purposes of illustration only and without limiting the scope of the present invention,

the cam surfaces 210 and 214 extend through approximately 40 while the surfaces 212 and 216 extend through approximately 90".

As shown in Fig. 8, the surfaces 210 and 212 are axially spaced, being separated by a drop-off or wall 218. Similarly, the axially spaced surfaces 214, 216 are separated by a wall 220. Each of the surfaces 212 andv 216 terminates in a recess 222, 224, respectively,

which are substantially diametrically opposed with respect to each other and are adapted to receive the followers 196, 198. A stop projection 226 is located adjacent the surface 219 remote trom the wall 218 for limiting rotational movement of the follower 196 in one direction. A second stop 228 located adjacent the surface 214 remote from the wall 220 limits the rotational movement of the follower 198 in one direction. It will be apparent from the above description that for any position to which the follower 196 is moved with respect to the surfaces 210, 212, the follower 198 will occupy a similar position with respect to the surfaces 214, 216 diametrically opposed to that of the follower 196.

A stop plate 230 is secured to the inner surface of the flange 202 and includes a pair of diametrically opposed stops 231 (only one of which is shown in Figs. 6 and 8) which guide the positioning of the followers 196, 198 upon the surfaces 210, 214 respectively. Stop plate 230 is so formed as to have two edges 232, for a purpose to be described hereinafter.

The shaft 188 extends slidably and rotatably through the open center of the annular cam assembly 200 so that the axial movement of the shaft 188 in one direction is limited by engagement of the followers 196, 198 with the cam assembly 280. The length of the shaft 142 and plunger 180 is such that when the followers 196, 198 are positioned within recesses 222, 224, the valves 34 and 58 will be in the position shown in Fig. 6. Spring 132 is stronger than spring 62, therefore, valve 58 will be biased to an open position while the valve 34 is urged by spring 38 to a closed position. However, when plunger 188 is moved axially to move the followers 196, 198 out of recesses 222, 224, shaft 142 is moved against the bias of spring 152 to space the valve elements 34 and 58 in various controlling positions as will appear hereinafter. If the shaft 188 is rotated after it has moved the valve members 34 and 58 to their various controlling positions, the followers 196, 198 will engage helical surfaces 210, 214 and valve members 34 and 58 will be retained in their controlled positions.

It will be apparent that the axial thrust exerted on the shaft 142 and plunger 188 from spring 152 will be transmitted directly to the followers 196, 198. Since the helical surfaces 210 through 216 are disposed at an angle to the line of action of this force, a portion of the force will be transformed in torque and will tend to transform the shaft 188 with accompanying slidable movement of the followers 196,198 down the surfaces 210 through 216. However, the helical surfaces 218 through 216 will exert a reactive force on the followers 196, 198, a portion of which will comprise a torsional component acting in a direction to resist such slidable action of the followers 196, 198.

The coacting surfaces of the followers 196, 198 and the relatively stationary cam assembly or detent member 200 can be so arranged that the operating force acting upon the movable plunger 180 will produce a component of force substantially equal in magnitude and opposite in direction to the reactive component of force resulting from friction between the surfaces regardless of the magnitude of the operating force of spring 152. With such an arrangement, an extremely small force may be utilized to slide the followers 196, 198 along the stationary cam assembly or detent member 200.

It is desirable that the frictional or resistive force resulting from the friction between follower 196 and the surfaces 210, 212 be equal to the component of force acting in parallel to the surfaces 210, 212 which tend to move the follower 196 along the same. This relationship may be stated in another way: the helix angle which the helical bearing surfaces makes with the plane perpendicular to the axis thereof is made such that the tangent thereof is substantially equal to the coefiicient of friction of the coacting surfaces of the followers 196 and the surfaces 210, 212.

Similarly, the resistive force resulting from friction between follower 198 -and the surfaces 214, 216 willbe equal to the component of force acting in parallel to the surfaces 214, 216 which tend to move the follower '198 along the surfaces 214, 216. In this manner, the tangent of the helix angle between the bearing surfaces 214, 216 and the axis thereof is substantially equal to the methcient of friction of the coacting surfaces of the follower 198 and the surfaces 214, 216.

From the foregoing, it will be apparent that the total torque acting on the shaft 188 as a result of the axial load thereon will be determined by the summation of the tendency for slidable movement produced by engagement of the followers 196,198 with the helical surfaces 210 through 216 and the tendency to resist slidable movement therebetween. Thus, rotation of the shaft 188 may be effected by the application thereto of a relatively small torque without regard to the magnitude of the axial thrust on the shaft 142.

Means is provided for applying a control force to the valve actuating means to effect release of a movable plunger 180 from the detent member 200. This means takes the form of an escapement control clock movement 234 disposed within the housing 186 and mounted therein by any suitable means. The movement 234 may be-of any conventional type and is here shown as including the driven gear 236 which meshes with a pinion 238 and being adapted to receive the shaft 180 so that the same may move axially relative to the pinion 238 while a torque transmitting relation is maintained therebetween. This connection is here shown as comprising a first leaf spring 240 secured atits medial portion to the pinion 238, a second leaf spring-242 secured at its medial portion to a boss 244 which in turn is secured to shaft 188 and the plate 194. The juxtaposed ends of the leaf springs 240, 242 are connected together at 246 so that rotational movement will be transmitted between the pinion 238 and shaft 188, but upon axial movement of the shaft 188, the springs 240, 242 will flex causingno axial displacement of the pinion 238.

Operation the position wherein the followers 196, 198 are-moved out of recesses 222, 224 beyond the outer extremities of the helical surfaces 210 through 216. The knob 190 is then rotated slightly until the followers 196, 198 engage the outer surface of the stop plate 230. The stop plates 231 serve to hold the plate 194 and the'followers 196, 198 away from the helical surfaces 210, 216 during a time setting operation. Rotation of the knob 190 is continued until the followers 196, 198 slip off the rear edge 232 of the plate 230 and on the surfaces 210, 214 respectively. Further rotation of the knob 190 is effective to move the followers 196, 198 along the surfaces 210, 214 until the same abuts the stops 226, 228 respectively as shown in Fig. 8.

Due to the movement of the shaft 142 against the bias of spring 152, the collar 144 will cause the levers 126, 136 to move the valves 34 and 58 to their dotted line positions shown in Fig. 6 and collar will permit latches 156, 158 to rotate clockwise under the action of springs 162, 164 respectively to communicate recesses with latch portions 129, 137 of levers-126, 136 to prevent return to their original positions. When the valves are in this position, fuel will flow from inlet 11 into chamber 20, around the valve 34, into chamber 18, through outlet 12 and to the afterburner (not shown). Since the valve 58 is in engagement with the valve seat 56, fuel will be prevented from flowing into chamber 46 to outlet 13.

As hereinbefore pointed out, the helix angles of the helical surfaces 210, 214 are such that the tendency towards rotational movement of the shaft 188 is balanced by the frictional force resisting such movement. The plunger 180 will, therefore, remain in the position in which it has been set unless an additional torque is applied thereto to start rotation of the same and move the followers 196, 198 down the surfaces 210, 214 toward recesses 222, 224 respectively.

The rotational setting movement of knob 190 also rotates the pinion 238 which drives the gear 236 and winds the mainspring (not shown) of the-clock movement 234. When the knob is released, the torque of the mainspring is transmitted directly to the gear 236 and the pinion 238, the escapement mechanism (not shown) of the timer movement 234 controlling the speed of rotation of the pinion 238, the plate 194, the shaft 188 and the knob 190 to their initial angular positions.

In the original setting of the knob 190, the followers 196, 198 are positioned adjacent the stops 226, 228 as shown in Fig. 7 in the solid line position D. After a predetermined time interval, depending upon the angu lar extension of the surfaces 210, 214 and the speed of the timer movement 234, the mainspring (not shown) will rotate the shaft 188 and the plate 194 and move the followers 196, 198 to the positions shown in dotted line B (Fig; 7). In moving to these positions, the plunger 180 has moved axially a distance indicated at F and consequently has moved collar 150 into engagement with release arm 166 as shown in Fig. 5.

In the positions indicated at E, the followers 196, 198 are disengaged from the helical surfaces 210, 214 and, since the followers are in alignment with walls 218, 220, the Plunger 180 will be moved rapidly to the right, as viewed in Fig. 6 for a distance indicated at I (Fig. 7) until the followers 196, 198 engage the helical surfaces 212, 216 adjacent the walls 218, 220 at the position indicated at K. Simultaneous with this axial movement of the plunger 180, collar 150, by engagement with release arm 166, rotates latch 156 in a clockwise direction to disengage the recess 160 of latch 156 from latch portion 129 of lever 126. Consequently, lever 126 under the action of spring 132, will engage stem 60 to bias valve 58 to the full line position of Fig. 6. When the valves are in this position, fuel will continue to flow from inlet 11, through chamber 20, around valve 34, to chamber 18 and through outlet 12 to the afterburner (not shown). However, fuel will also flow around valve 58, into chamber 46 and through outlet 13 to the main burner (not shown).

Continued rotation of shaft 188 and plate 194 under the torque of a mainspring (not shown) of the timer movement 234 moves followers 196, 198 along the surfaces 212, 216 to the positions indicated in dotted lines (Fig. 7) after a predetermined time interval set by angular extensions of the surfaces 212, 216 and the speed of the timer movement 234. In the movement of the followers 196, 198 to the positions indicated at O, the plunger 180 will have moved a distance P.

In the position indicated at O, the followers 196, 198 are disengaged from the helical surfaces 212, 216 and, since the followers 196, 198 are then in alignment with the recesses 222, 224 the plunger 180 will be moved rapidly to the right, for a distance indicated at T until the followers 196, 198 engage the bottom of recesses 222, 224. Simultaneous with this axial movement of plunger 180, collar 150 will engage a release arm 168 to rotate latch 158 in a clockwise direction to disengage recess 160 from latch portion 137 of inlet valve lever 136. Spring 38 will then urge valve 34 against seat 32 When followers 196, 198 move into recesses 222, 224,

2,91 a,oas

further rotation of the shaft is prevented. The clock movement 234 will then stall and further unwinding of the mainspring is prevented. Thus, the mainspring will never be permitted to'run down and a substantial torque maybe exerted thereby on the shaft 188 in all angular positions of the shaft 188 to eliminate any danger of insufficient winding of the mainspring when the timer is set to operate at a small time interval. It is to be noted that since the followers 196, 198 are diametrically opposed to each other, they will engage and disengage the helical surfaces 210, 216 simultaneously thereby preventing possible tilting and binding of the plunger 180.

It will be apparent from the foregoing that the embodiment provides a new and improved control device which permits sequential timed actuation of a plurality of control valves for controlling fuel flow to a plurality of burners, all within a single casing. It will also be obvious to those skilled in the art that the illustrated embodiment may be variously changed and modified, or features thereof singly or collectively embodying other combinations than those illustrated without departing from the scope of the invention or sacrificing all of the advantages thereof, and accordingly, the disclosure herein is illustrative only and the invention is not limited thereto.

I claim:

1. In a control device for fluid fuel burners or the like, the combination comprising a casing having an inlet passage and a plurality of outlet passages therein intersected by a plurality of valve seats, a plurality of valve members in said casing sequentially movable between open and closed positions relative to the valve seats, means associated with said valve members for biasing the same in one direction relative to said seats, a pair of separate rotatably mounted levers in said casing cooperable with said valve members for moving said valve members in the opposite direction relative to said seats, an actuating member operatively connected to said levers and being movable in one direction for imparting rotation thereto in one direction, said actuating member being movable in the other direction to cause sequential rotation of said levers in the other direction.

2. In a control device, the combination comprising a casing having an inlet and outlet passages therein intersected by a pair of valve seats, an inlet valve member movable between open and closed positions relative to one of the valve seats, an outlet valve member movable between open and closed positions relative to the other valve seat, a pair of levers rotatably mounted in said casing for controlling the movement of said valve members, an actuator operably associated with said levers and being operable when moved in onerdirection through a predetermined range of movement to rotate said levers to a predetermined position for moving said inlet valve member to said open position and said outlet valve member to said closed position, latch means operably associated with said levers to hold said levers in said predetermined position, and means operably associated with said actuator for controlling said latch means to effect sequential release of said levers by said latch means and thereby effect sequential opening and closing of said outlet valve member and said inlet valve member respectively.

3. A control device comprising a casing having an inlet passage and outlet passages therein, valve seats in said casing intersecting said inlet passage and one of said outlet passages, valve members movable between open and closed positions relative to the valve seats, resilient means associated with said valve members normally biasing same to said closed position, lever means rotatably mounted in said casing and being cooperable with said valve members for controlling the movement thereof, an

actuator operably associated with said lever means for imparting rotation thereto and being operable when moved in one direction to rotate said lever means to a predetermined position and thereby move one of said valve members to said open position and another of said valve members to said closed position, latch means operably associated with said lever means for retaining said lever means in said predetermined position, and means operably associated with said actuator for controlling said latch means for sequentially releasing said lever means from said latch means to effect sequential movement of one of said valve members to said open position and another of said valve members to said closed position.

4. In a control device, the combination comprising a casing having an inlet passage and outlet passages therein, a pair of valve seats intersecting said inlet passage and one of said outlet passages, a pair of valve members movable between open and clo'sed positions relative to said valve seats respectively, a cover detachably secured to said casing, a pair of lever means operatively connected to said cover and being operable to control the movement of said valve members, an actuator carried by said cover for moving said lever means to a predetermined position, latch means for retaining said lever means in said predetermined position, and means on said actuator for engagement with said latch means on return of the actuator to its original position for releasing said lever means sequentially.

5. In a control device, the combination comprising a casing having an inlet and a plurality of outlets therein, a first valve normally biased to close said inlet and a second valve normally biased to close one of said outlets, a detachable cover for said casing having a bridge attached thereto, means forming a relieved portion in said bridge communicating with another of said outlets, a pair of levers rotatably mounted on said bridge for controlling movement of said first and second valves respectively, an actuating shaft slidably mounted in said cover having a first means for moving said pair of levers to open said first valve and close said second valve, latch means for retaining said pair of levers in said moved position, and a second means on said actuating shaft engageable with said latch means for effecting a sequential release of said pair of levers to open said second valve and then to close said first valve.

6. In a control device, the combination comprising a casing having an inlet and an outlet passage therein intersected by a pair of valve seats, an inlet valve member movable between open and closed positions relative to one of said valve seats, an outlet valve member movable between open and closed positions relative to the other of said valve seats, a pair of levers rotatably mounted in said casing for controlling the movement of said valve members, an actuator associated with said levers and being operable when moved in one direction through a predetermined range of movement to rotate said levers to a predetermined position and move said inlet valve member to said open position and said outlet valve member to said closed position, latch means associated with said levers to hold the same in said predetermined position, said actuator being movable in the other direction to eifect sequential release of said levers by engagement with said latch means and thereby effecting sequential opening and closing of said outlet valve member and said inlet valve member respectively.

7. In a control device, the combination comprising a casing having an inlet and an outlet passage therein intersected by a pair of valve seats, an inlet valve member movable between open and closed positions relative to one of said valve seats, an outlet valve member movable between open and closed positions relative to the other of said valve seats, a pair of levers rotatably mounted in said casing for controlling the movement of said valve members, an actuator associated with said levers and being operable when moved in one direction to rotate said lovers to a predetermined position and move said inlet valve member to said open position and said outlet valve member to said clo'sed position, latch means associated with said levers to hold the same in said predetermined position, and a collar on said actuator for engagement with said latch means to release said levers sequentially upon return of said actuator to its original position thereby effecting sequential opening and closing of said outlet valve member and said inlet valve member respectively.

References Cited in the file of this patent UNITED STATES PATENTS 1,715,125 Feit May 28, 1929 2,192,193 Johnson Mar. 5, 1940 2,341,940 Millington Feb. 15, 1944 2,726,717 Strobel Dec. 13, 1955 2,778,419 Wantz Jan. 22, 1957 2,810,435 Demi et a1. Oct. 22, 1957 

